A planetary gearbox

ABSTRACT

Parallel shafting gearbox have problems like the frictional losses, gear shifting is very hard under load, wear and tear of gears while shifting and operating of the gears, load distribution on single driven gear and it is hard to derive large reductions gear ratio easily. Present invention introduces a gearbox as a solution for above problems using PGTU (planetary gear trains unit)s such that all the PGTUs in gear box are connected serially with axles on which planetary gears are mounted, of the PGTUs which are arranged between them, forming a series of CPCAs, for transmission from rotating driving shaft on which sun gears are mounted to the driven shaft by braking the motion of the ring gear of PGTU through which the transmission is to be carried out while setting free the ring gears of rest of the PGTUs in the gear box, It is useful in automobile vehicle etc.

FIELD OF INVENTION

The present invention relates to gear box for motor vehicle using planetary gear train units.

BACKGROUND OF INVENTION

In transmission system of an automobile vehicle it is known that a gear box is used which is usually having a parallel axial shafting in which complete load distribution is on single driven gear, also gear cannot be shifted under load and large reductions are very hard to derive. While shifting and operation of gears wear and tear of gear takes place which leads to grinding of gear, in constant mesh gear box wear and tear of dog takes place; one of the most important disadvantage of parallel shafting is that the frictional losses are more as compare to planetary or epicyclic gear train transmission, also in many cases overall dimensions of known art are too great.

OBJECT OF THE INVENTION

The principle object of the present invention is to introduce a gear box which will minimize the frictional losses, another object of the invention is to make possible gear shifting under load and to reduce or nullify wear and tear of gears while shifting and operating of the gears, further object of the invention is to reduce load distribution on single driven gear and to derive large reductions gear ratio easily.

SUMMARY OF INVENTION

Present invention introduces a gear box using PGTU (planetary gear trains unit)s such that the sun gears of all the PGTUs are mounted on driving shaft and carrier arm CPCA (circular planet carrier arm)s of all the PGTUs in gear box are connected serially with axles on which planetary gears are mounted, of the PGTUs which are arranged between them, forming a series of CPCAs which is fixed to the carrier arm disc to the center of which the driven shaft is fixed. By braking the motion of the ring gear of PGTU through which the transmission is to be carried out while setting free the ring gears of rest of the PGTUs in the gear box, and thus allowing to rotate all the carrier arms along with driven shaft in same manner that of the carrier arm of PGTU of which ring gear is braked and through which transmission is being carried out when driving shaft is rotating.

In another form of invention the above mentioned planetary gear box is characterized with an additional PGTU comprises one driving gear train and one driven gear train having their ring gears fixed rigidly to each other, and it is connected to CPCAs series by fixing driven sun gear to CPCA of the CPCAs series rigidly and by braking the revolutionary motion of planet gears of this additional PGTU through which the transmission is to be carried out while setting free the ring gears of rest of the PGTUs in the gear box, and thus allowing to rotate all the carrier arms along with driven shaft in the same manner that of the driven sun gear of additional PGTU of which revolutionary motion of planet gears of both the gear trains is braked and through which transmission is carried out when driving shaft is rotating.

In another form of invention an additional PGTU T3 is characterized with a socket Carrier arm (SCA) and pins which can attach ring gear of driven gear train to driving Sun gear directly and by braking the revolutionary motion of planet gear of driven gear train and setting unbraked the revolutionary motion of planet gear of driving gear train the reverse motion transmission is carried out when driving shaft is rotating and ring gears of the rest of the PGTUs are set free.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 shows a gearbox using planetary gear train units

FIG. 2 shows a series SR of CPCAs (circular planetary gear arms).

FIG. 3 shows a common diagram of brakes 111,211,311, and 411.

FIG. 4 shows a PGTU3 (Planetary gear train unit 3).

FIG. 5 shows a series SR1 of CPCAs (circular planetary gear arms).

FIG. 6 shows a gearbox using planetary gear train units characterized with PGTU3.

FIG. 7 shows a circular socket arm mechanism.

FIG. 8 shows a gearbox using planetary gear train units characterized with PGTU3 and a socket carrier arm mechanism.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS OF INVENTION

Referring to the FIG. 1, can be seen that a planetary gear box comprising, a driving shaft 1, a driven shaft 2, planetary gear train units T1 and T2, disc brakes 111 and 211 and base W

Shaft supports A and B with brake supports 115 and 215 stands on a base W, the side/end in the direction of support A from support B of gear box and of all the parts within is termed as its side A/end A and the side/end in the direction of support B from support A of gear box and of all the parts within is termed as its side B/end B

PGTU (planetary gear train unit) T1 comprises a sun gear 101 mounted on driving shaft 1, planet gears 102 and 103 which are meshed with sun gear 101 and mounted on bearings 104 and 105 respectively which are mounted on axles 106 and 107 respectively, ends A of both the axles are fixed to side B of CPCA (circular planet carrier arm) 108 and ends B of both the axles are fixed to the side A of circular planet carrier arm 208, ring gear 110 which is coaxial with sun gear 101 and is meshed with planet gear 102 and 103.

PGTU T2 comprises a sun gear 201 mounted on driving shaft 1, planet gears 202 and 203 which are meshed with sun gear 201 and mounted on bearing 204 and 205 respectively which are mounted on axles 206 and 207 respectively, ends A of both the axles are fixed to side B of CPCA (circular planet carrier arm) 208 and ends B of both the axles are fixed to the side A of carrier arm disc 3, ring gear 210 which is coaxial with sun gear 201 and meshed with planet gear 202 and 203.

Driven shaft 2 of which end A is fixed at the center of the side B of carrier arm disc 3 to its center and near its end B it is mounted on support B with bearing 5. It is the out put shaft of the gearbox

Driving shaft 1 near its end A it is mounted on support A with bearing 4. On driving shaft 1, sun gear 101 and 201 are mounted. It is the input shaft of the gearbox

Circular planet carrier arms (CPCAs) 108 and 208 are mounted on bearing 109 and 209 respectively which are mounted on driving shaft 1.

CPCA series SR as shown in FIG. 2 consist of CPCAs 108,208, carrier arm disc 3, axles 106,107,206 and 207, CPCAs 108 and 208 are connected to each other with axles 106 and 107, ends A of both the axles are fixed to side B of CPCA (circular planet carrier arm) 108 and ends B of both the axles are fixed to the side A of circular planet carrier arm 208, CPCAs 208 and carrier arm disc 3 are connected to each other with axles 206 and 207, ends A of both the axles are fixed to side B of CPCA (circular planet carrier arm) 208 and ends B of both the axles are fixed to the side A of carrier arm disc 3.

Disk brake 111 as shown in FIG. 3 comprising, rotor (brake disc) 112 mounted on ring gear 110, caliper sides 116 and 117 which holds brake pads 118 and 119 on the side A and B respectively of the rotor (brake disc) 112, bar 113 of which end C is fixed to the side A of caliper side 116 with knuckle joint and bar 113 is fixed at a point O1 with pin joint to the bar 114 and at point X1 with a knuckle joint to guide pin (Slide pin) arm 122 of guide pins (Slide pins) 120 and 121 which are passed through ports/passage 123 and 124 respectively and are connected to the caliper side 117, end D of the bar 113 is free to push or pull along the direction of support A and B and bar 114 is fixed at its end D to support 115.

Disk brake 211 as shown in FIG. 3 comprising, rotor (brake disc) 212 mounted on ring gear 210, caliper sides 216 and 217 which hold brake pads 218 and 219 on the side A and B respectively of the rotar (brake disc) 212, bar 213 of which end C is fixed to the side A of caliper side 216 with knuckle joint and bar 213 is fixed at a point O2 with pin joint to the bar 214 and at point X2 with a knuckle joint to guide pin (Slide pin) arm 222 of guide pins (Slide pins) 220 and 221 which are passed through ports/passage 223 and 224 and are connected to the caliper side 217, end D of the bar 213 is free to push or pull along its path through the direction of support A to B bar 214 is fixed at its end D to support 215.

FIG. 1 shows a planetary gear box, in case 1 when driven shaft 2 is set free of load, where the transmission is being carried out through the PGTU T1, As driving shaft 1 rotates sun gears 101 and 201 are also rotated which makes planet gears meshed with them to revolve about them which further makes to rotate the corresponding ring gears 110 and 210, simultaneously resulting in rotating the circular carrier arm 108 and 208 with carrier arm disc 3 along with driven shaft 2 in same speed (rpm) that of 1.

when brake rod 113 is pulled along its path from direction of support B to direction of support A then caliper side 116 and 117 presses the brake pads 118 and 119 on rotor (brake disc) 112 braking the motion of rotor (brake disc) 112 and hence the motion of the ring gear 110 of PGTU T1 is braked. As driving shaft 1 rotates sun gears 101 is also rotated which tries planet gears meshed with it to revolve about it along with the ring gear 110, but as the ring gear 110 is braked the motion of sungear 101 results in displacement of planet gears with their rotation about their corresponding own axes of rotation and simultaneously the revolution of planet gears about sungear 1, and at the same time ring gears of rest of the PGTUs in the gear box are set free, and thus it allows to rotate all the CPCAs (circular planet carrier arms) and carrier arm disc 3 along with driven shaft in same manner that of the circular planet carrier arm 108 of PGTU T1 and the ring gear of the rest of the PGTUs rotates in speed (rpm) resulted by the motion of corresponding sun gear, planet gear and Circular planet carrier arm. Hence transmission is carried out through PGTU T1 when driving shaft 1 is rotating.

In case 2 when driven shaft 2 is braked by some load then carrier arm disc 3 with circular planet carrier arm 108 and 208 are also braked, As driving shaft 1 rotates sun gears 101 and 201 are also rotated which tries planet gears meshed with them to revolve about them, but as CPCAs (circular planet carrier arms) 108 and 208 are braked it results in rotation of planet gear 103 and 104 about their corresponding own axes which further makes to rotate the corresponding ring gears 110 and 210 in speed (rpm) resulted by the motion of corresponding sun gear and planet gear.

when brake rod 113 is pulled along its path from side B to side A then caliper sides 116 and 117 presses the brake pads from both sides of rotor (brake disc) 112 on rotor (brake disc) 112 braking its motion and hence the motion of the ring gear 110 of PGTU T1 is also braked. As in this case CPCA (circular planet carrier arm) 108 is already braked when the driving shaft 1 rotates sun gears 101 is also rotated which tries to rotate planet gears about their own axis with the rotation of the corresponding ring gears 110 but as the ring gear 110 is also already braked the motion of sungear 101 results in displacement of planet gears 103 and 104 with their rotation about their own axis of rotation and simultaneously the revolution of planet gear about sungear 101, and at the same time ring gears of rest of the PGTUs in the gear box are set free, and thus it allows to rotate all the CPCAs (circular planet carrier arms) and carrier arm disc 3 along with driven shaft in same manner that of the CPCA (circular planet carrier arms) 108 of PGTU T1 and the ring gear of the rest of the PGTUs rotates in rpm (speed) resulted by the motion of corresponding sun gear, planet gear and Circular carrier arm

In another form of invention Referring to the FIGS. 4 and 6, can be seen that A planetary gear box as described above is characterized with an additional PGTU T3, brakes 311 and 411, rods 310 and 410, rods 417 and 418 wherein PGTU T3 comprising of one driving planetary gear train E1 and one driven planetary gear train E2 as shown in FIG. 4, of which planetary gear train E1 consist of sun gear 301 mounted on driving shaft 1, planet gears 302 and 303 mounted on bearing 304 and 305 respectively which are mounted on end B of axles 306 and 307 respectively, end A of both the axles 306 and 307 are fixed to side B of circular planet carrier arm (CPCA) 308, ring gear 310 which is coaxial with sun gear 301 and is meshed with planet gear 302 and 303, Planetary gear train E2 consist of sun gear 401 mounted on bearing 419 which is mounted on driving shaft 1, planet gear 402 and 403 mounted on bearing 404 and 405 respectively which are mounted on end A of axles 406 and 407 respectively end B of both the axles 406 and 407 are fixed to side A of circular planet carrier arm (CPCA) 408, ring gear 410 which is coaxial with sun gear 401 and is meshed with planet gear 402 and 403; Ring gear 310 is fixed rigidly to Ring gear 410 with rods 309 and 409 by connecting side A of both the rods to side B of ring gear 310 and side B of both rods to side A of ring gear 410 rigidly;

PGTU T3 is connected to the CPCAs series SR as shown in FIG. 5, by connecting end A of both the rods 417 and 418 to side B of Sun gear 401 and end B of both rods to side A of CPCA 108 rigidly and making sun gear 401 a part of series SR.

Disk brake 311 comprising, rotor (brake disc) 312 mounted on CPCA 308, caliper sides 316 and 317 which hold brake pads 318 and 319 on both the side of the rotor (brake disc) 312, bar 313 of which end C is fixed to the caliper side 316 with knuckle joint and bar 313 is fixed at a point O3 with pin joint to the support 314 and at point x3 with a knuckle joint to guide pin arm 322 of guide pins 320 and 321 which are passed through passage 223 and 224 and connected to the caliper side 317, end D of the bar 313 is free to push or pull along the direction of support A and B.

Disk brake 411 comprising, rotor (brake disc) 412 mounted on CPCA 408, caliper sides 416 and 417 which hold brake pads 418 and 419 on both the side of the rotor (brake disc) 412, bar 413 of which end C is fixed to the caliper side 416 with knuckle joint and bar 413 is fixed at a point o4 with pin joint to the support 414 and at point x4 with a knuckle joint to guide pin arm 422 of guide pins 420 and 421 which are passed through passage 223 and 224 and connected to the caliper side 417, end D of the bar 413 is free to push or pull along its path through the direction of support A to B.

FIG. 6 shows planetary gear box characterized with PGTU T3, in case 1 when driven shaft 2 is set free of load, where the transmission is being carried out through the PGTU T3, as driving shaft 1 rotates sun gears 301 also rotates which makes planet gears 302 and 303 meshed with them to revolve about it which further makes to rotate the corresponding ring gears 310 and it also rotate ring gear 410 in the axis of rotation that of ring gear 310 as it is rigidly fixed to ring gear 310, which makes planet gears 402 and 403 meshed with ring gear 410 to revolve about the axis of rotation that of ring gear 410 which further rotates sun gear 401 in the axis of rotation that of 410 and simultaneously resulting in rotating the CPCAs series SR, with carrier arm disc 3 and driven shaft 2 in same speed (rpm) that of driving shaft 1.

In case 2 when driven shaft 2 is braked by some load then carrier arm disc 3 with circular planet carrier arm 108 and 208 along with Sungear 401 are also braked, As driving shaft dl rotates sun gears 301 also rotates which makes planet gears 302 and 303 meshed with it to revolve about it which further makes to rotate the corresponding ring gears 310 and it also rotate ring gear 410 in the axis of rotation that of ring gear 310 as it is rigidly fixed to ring gear 310, which makes planet gears 402 and 403 meshed with ring gear 410 to revolve about the axis of rotation that of ring gear 410 which further tries to rotates sun gear 401 in the axis of rotation that of 410 but as Sungear 401 is already braked it results in displacement of planet gears 402 and 403 meshed with sungear 401 with their rotation about their own corresponding axes of rotation and their revolution about sungear 401, which makes CPCAs 308 and 408 rotate in speed resulted by the motion of corresponding sun gears and planet gears.

when brake bar 313 and 413 are pulled along their paths from direction of support B to direction of support A then their corresponding caliper sides presses the brake pads from both sides of rotor (brake disc) 312 on rotor (brake disc) 312 and that of rotor (brake disc) 412 on rotor (brake disc) 412 respectively braking their motions and hence the motion of the CPCAs 308 and 408 of PGTU T3 are braked. As driving shaft 1 rotates sun gears 301 is also rotated which tries planet gears 302 and 303 meshed with it to revolve about it along with the ring gear 310 but as the CPCA 308 is already braked the motion of sungear 301 results in rotation of planet gears 302 and 303 meshed with it about their own axis of rotation in reverse direction that of motion of sungear 301 which makes ring gear 310 to rotate in reverse direction that of motion of sungear 301 and it also rotate ring gear 410 in reverse direction that of motion of sungear 301 along the axis of rotation that of 310 as it is rigidly fixed to 310, which tries to make planet gears 402 and 403 meshed with ring gear 410 to revolve about the axis of rotation that of ring gear 410 but as CPCA 408 is already braked the motion of ring gear 410 results in rotation of planet gears 402 and 403 meshed with it about their own corresponding axes of rotation in same direction that of motion of ring gear 410, which makes sungear 401 to rotate in same direction that of motion of sungear 301, and at the same time ring gears of rest of the PGTUs in the gear box are set free, and thus it allows to rotate all the circular carrier arms and carrier arm disc 3 along with driven shaft 2 in same manner that of the Sungear 401 of PGTU T3 and the ring gears of the rest of the PGTUs rotates in rpm (speed) resulted by the motion of corresponding sun gear, planet gear and Circular carrier arm. In this way the transmission is carried out through PGTU T3 when driving shaft 1 is rotating.

In another form of invention referring to FIG. 7 can be seen that an additional PGTU T3 characterized with socket carrier arm between the gear train E1 and E2 comprising pins 502 and 503 mounted on side B of Sungear 301, a socket carrier arm SCA 501 with pin sockets 504 and 505, rod socket 506 and 507 through which rods 309 and 409 are passed, shaft sockets 508 at the centre through which driving shaft 1 is passed, guide rings 509 and 510 on side A and B of CSCA 501 respectively at a particular distance from SCA, which are supported by guide ring holder 511 with its wing 512 and wing 513 fixed to the guide rings 509 and 510 respectively guide ring holder 511 have a track slot 514 at its bottom, track 515 is fixed on base W on which track slot 514 is placed.

When guide rings holder 511 is pushed from side A to side B then its displacement along the track 515 takes place which makes guide ring 510 to push SCA 501 in the same direction that of the displacement of ring holder 511 due to which SCA 501 comes near sungear 301 and hence pins 502 and 503 are inserted in pin socket 504 and 505, due to which the motion of sungear 301 makes rods 309 and 409 to revolve around driving shaft 1, causing ring gears 310 and 410 to rotate in the same direction that of the motion of sungear 301, at the same time the revolutionary motion of the planet gears 402 and 403 is braked by applying brake 411 and the revolutionary motion of the planet gears 302 and 303 is set unbraked which makes planet gears 402 and 403 to rotate in direction of rotation of sungear 301 and further rotates sun gear 401 in direction opposite of rotation of sungear 301 hence transmission is carried out through PGTU T3 in reverse direction of rotation of driving shaft 1 when driving shaft 1 is rotating. 

1-18. (canceled)
 19. A planetary gear box comprising: a driving shaft 1; plurality of planetary gear train unit (PGTU) arranged on the driving shaft 1, wherein each PGTU comprising of, a sun gear 101 mounted rigidly on the driving shaft 1; at least planet axle 106 connected to at least its circular planet carrier arm (CPCA) 108; at least a planet gear 102 rotatably mounted on its corresponding axle 106 and meshed with its corresponding sun gear 101; a ring gear 110 meshed with at least its corresponding planet gear 102; a carrier arm disc (CAD) 3, connected to one of the CPCA; a driven shaft 2, connected to CAD 3; at least a brake assembly for each ring gear.
 20. The planetary gear box as claimed in claim 19, wherein the plurality of CPCAs, planet axles 106 and CAD 3 are connected so forming a CPCA series called SR unit, wherein the rotation of any one CPCA 108 rotates the entire SR unit in the same direction and speed.
 21. The planetary gear box as claimed in claim 19, wherein the plurality of CPCAs, the CAD 3 of the SR unit, each have a polygonal shape.
 22. The planetary gear box as claimed in claim 19, wherein: the driving shaft 1 is mounted on bearing 4 within a through-holed port at the top of a shaft support A, and the bottom of the shaft support A is rigidly affixed on the base W; and the driven shaft 2 is mounted on a bearing 4 within a through-holed port at the top of a shaft support B, and the bottom of the shaft support B is rigidly affixed on the base W.
 23. The planetary gear box as claimed in claim 19, wherein rotational motion of the driving shaft 1 is transmitted to the driven shaft 2 having no load, by keeping ring gears unbraked.
 24. The planetary gear box as claimed claim 19, wherein rotational motion of the driving shaft 1 is transmitted through any one of the PGTU to the driven shaft 2 having a load, by braking rotational motion of its corresponding ring gear, while keeping ring gears of remaining PGTUs unbraked.
 25. A planetary gear box as claimed in claim 19, wherein the shaft 1 is a driven shaft and the shaft 2 is a driving shaft.
 26. A planetary gear box as claimed in claim 19 wherein: the planet gears are mounted rigidly on the planet axles; and the planet axles are rotatably affixed to at least a CPCA's or to CAD or to both
 27. A planetary gear box as claimed in claim 19, wherein the disc brake assembly 111 is adopted as brake assembly for at least a ring gear.
 28. The planetary gear box as claimed in claim 19, wherein rotational motion of the driving shaft 1 is transmitted through the third PGTU T3 to the driven shaft 2 having no load, by keeping ring gears of all the PGTUs (T1, T2 and T3) unbraked.
 29. The planetary gear box comprising two planetary gear boxes as claimed in claim 19 connected to each other, wherein a driven shaft of a first planetary gear box is affixed to a driving shaft of a second planetary gear box, and wherein a driving shaft of the first planetary gear box is the driving shaft of the combination planetary gear box and a driven shaft of the second planetary gear box is the driven shaft of the combination planetary gear box.
 30. The planetary gear box as claimed in claim 29, wherein the rotational motion of the driving shaft 1 is transmitted through the third PGTU T3 to the driven shaft 2 having a load, by braking rotational motion of the CPCA 308, and CPCA 408, and keeping rotational motion of the ring gears of remaining PGTUs unbraked.
 31. The planetary gear box as claimed in claim 29, wherein the third PGTU T3 comprises a reverse gear mechanism comprising: a socket carrier plate 501 positioned between the driving gear train E1 and the driven gear train E2; a first guide ring 510 arranged on a side A of the socket carrier plate 501 and a second guide ring 509 arranged on a side B of the socket carrier plate 501; a shaft port 508 in the center of the socket carrier plate 501, the driving shaft slid through the shaft port 508; a first axle port 506 and a second axle port 507, the seventh 309 and eighth 409 axles slid through the first 506 and second 507 axle ports respectively; and a pair of pin ports (504 and 505), wherein the shaft port 508, the first 506 and second 507 axle ports, and the first 504 and second 505 pins ports are diametrically aligned; a pair of pins (502 503) rigidly affixed to the side B of the third sun gear 301 at positions enabling the pair of pins to slide in the pair of pin ports; a guide ring holder 511 affixed on the base W, the guide ring holder 511 including: a first wing 513 supporting the first guide ring 510 thereon at a top end of the guide ring holder 511, a second wing 512 supporting the second guide ring 509 thereon at the top end of the guide ring holder 511, a slot 514 at a bottom end of the guide ring holder 511, and a track 515 rigidly affixed on the base W and slid through the slot
 514. 32. The planetary gearbox as claimed in claim 19, wherein the planetary gear box comprises a third planetary gear train unit (PGTU) T3, comprising: a driving planetary gear train E1 comprising, a sun gear 301 fixedly mounted on the input shaft 1; at least a planet axle 306 affixed to a CPCA 308; at least a planet gear 302 rotatably mounted on planet axle 306 and meshed with the third sun gear 301; at least ring gear 310 meshed with the planet gear 302; a driven planetary gear train E2 comprising, at least seventh axle 309 and an eighth axle 409, an end A of each of the seventh axle 309 and eighth axle 409 affixed to a side B of the third ring gear 310; at east a sun gear 401 rotatably mounted on the input shaft 1; at least an axle 406 affixed to CPCA 408; at least a planet gear 402 rotatably mounted on planet axle 406 and meshed with sun gear 401; a fourth ring gear 410 meshed with at least planet gear 402; Ring gear 310 is fixed to ring gear 410; sungear 401 is fixed to at least a CPCA of CPCA series SR unit at least brake assembly for CPCA 308; at least a brake for CPCA
 408. 33. The planetary gear box as claimed in claim 32 wherein the rotational motion of the driving shaft 1 is transmitted through the reverse mechanism of PGTU T3 to the driven shaft 2 having a load by locking the pair of pins (502, 503) in the pair of pin sockets (504, 505) and braking the third 310 and fourth 410 ring gears, while keeping the ring gears (110, 210) of the rest of the PGTUs (T1, T2) in the gear box unbraked.
 34. The planetary gear box as claimed in claim 29 wherein only PGTU T3 is present in the planetary gear box. 